Conveyer driving mechanism



Sept. 25, 1934. M. LOW

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CONVEYER DRIVING MECHANISM Filed June 25, 1931 6 Sheets-Sheet 3 1a yo f 49 I 91/; a

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Sept. 25, 1934. M. LOW 1,974,826

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Sept. 25, 1934. M. LOW

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PatentedySept. 25, 1934 w I v UNITED; STATES PATENT OFFICE CQNVEYER DRIVING DIEOHANISM Marshall Low, Washington, D. 0., assignor to I Hartford-Empire Company, Hartford, Conn., a corporation of Delaware 7 Application June 25, 1931, Serial No. 546,860

. Claims. (01. 198-202 This invention relates to conveyer driving For example, if 'two interconnected helices only mechanism and it has particular relation to mechare considered, and one is held against longitudianism for driving and supporting conveyers andnal movement and at the same time is rotated belts fabricated from a plurality of intercon- 360, it will force the other helix longitudinally I nected laterally extending wire helices. a distance equal to one pitch in the same man- Heretofore, great inconvenience has been enner as two members having screw-threaded encountered .by the inherent tendency for a congagement with one another. If a section of aconveyer or belt of the type mentioned to creep veyer having a length equal to thecircumference transversely on the driving drum or supporting of a drum is wrapped about the drum, it will be 0 roller with which the conveyer frictionally ennoted that the abutting ends of the section will gages. This tendency is caused by the turn or be offset laterally relative to one another a distwist of the individual helices as they succestance equal to the pitch of the helices of which sively frictionally engage the tractive surface of such section is fabricated. In this case, the 360 the drum at the line of tangency between the of rotation necessa y for this a ount Of lateral l5 plane of the article bearing strand of the condisplacement is dividedequally between each of veyer and the circumference of the driving drum the several helices of which the section is fabrior roller, and then change their direction of cated and each of these helices is displaced relatravel from a rectilinear direction to a curvilintive to each other an amount proportional to the ear direction. When any given helix of a conrelative angular displacement therebetween.

20 veyer of this type engages a driving drum hav- However, a conveyer is seldom in contact with a ing a tractive surface, the friction therebetween drivin drum o ore t an three-fourths of its is suflicient to prevent any longitudinal or axial circumferential area and conseque each movement of the helix, and consequently as it rotation of the drum the conveyer will creep latchanges its direction of movement in conform- 3 the drum 6 distance equal to three- 25 ing to the curvature of the drum, each of its conf r of n p In h n instance, i th volutions exerts a camming or cork w ti pitch of the convolutions of the helices of the conupon the interconnecting convolutions of the veyer is th er Of an inch, for p the following helix, with the result that the following n y ill creep rally n i s upport, and helix is forced in a longitudinal direction relative 0n the drum nine-thirty seconds of an ch o 30 t th leading helix a d i l d t th drum each complete rotation of the drum, and if the laterally offset with respect thereto. This foldrum is two feet in diameter, for p the lowing helix then becomes the leading helix and conveyer Will creep laterally this di ta for ea h i t n becomes fixed on the drum as against fifty-four inches of'linear travel of the conveyer. longitudinal movement and exerts the camming Various D e fiS have been resorted to in 35 r corkscrew action upon t t following helix, order to avoid or counteract this inherent tendand this action is repeated as each helix engages y for a conveyer O this yp to Creep laterally the drum. If the. drum continuesto rotate, the b t P t e rtS in is direction have been exconveyer will eventually creep laterally on the ve d not e y s ccessful. drum to such an extent that either the edge of Such expedientsare exemplified in the Swins-- 40 the conveyer becomes deformed through friccoe Patent No. 712,212, in which one form of a. tionalengagement with other mechanism at the woven Wire conveyer is constructed of a plu-' side of the device or creeps entirely off of the drum a y of Sections, the helices 0f j e t Sections if free to do so. In short, the problem presents being woundin' pp di ect ons So that after a question of action and reaction in which the the conveyer has creeped laterally in one direc- 45 helix of the conveyer which is in engagement with tion a predetermined distance it is caused to creep the drum, being immovable in a longitudinal diin an opposite direction an equal distance. In rection, transmits axial movement to the next constructing a conveyer of this type, great infollowing helix as it is being led onto the drum. convenience, expense and manual labor is in- The amount of the longitudinal movement of each volved as it is first necessary to fabricate two con- 50 helix as it is led onto the drum or roller is deterveyers, one of right hand wound helices and anmined entirely by the pitch distance of the conother of left hand wound helices. The helices of volutions of the helices of which the conveyer each of these conveyers are clinched at their outer is fabricated and the diameter of the drum or endsto prevent them from becoming unwound or roller and the direction of creepage depends upon otherwise displaced in use. These conveyers are 55 whether the helices are right or left hand wound. then each separated into sections, each having an equal number of helices, and in doing so it is necessary to manually unclinch the ends of certain helices and unscrew such helix to separate the sections. The right and left hand sections are then arranged alternately and are secured together manually in various ways. Obviously, a conveyer constructed in this manner presents many undesirable features.

Also, an attempt has been made to overcome creepage by fabricating two conveyers each constructed of right and left hand wound wire helices as before, then separating the conveyers longitudinally, and then securing one-half of one conveyer to one-half of the other conveyer. This particular type of construction is also disclosed in the patent to Swinscoe previously referred to and is designed to offset the tendency for one longitudinal half of the conveyer to creep laterally in one direction by a tendency for the other half of the conveyer to creep laterally in an opposite direction. However, in such construction, if the left hand half of the conveyer, looking in the direction of movement of the conveyer, is constructed of right hand wound helices and the right hand half of the conveyer isconstructed of left hand wound helices, each 1ongitudinal half of the conveyer will creep toward the center with the result that the conveyer will buckle in the middle. On the other hand, if the positions of the longitudinal sections are reversed, there is a strong tendency to stretch the helices along the line of union between the two sections and eventually to separate the conveyer longitudinally. Various means have been attempted to prevent or counteract this tendency, such as by tying the helices together by rods or the like but obviously if this tendency is effectually prevented, the surface of the driving drum will become worn due to longitudinal slippage and eventually become useless.

According to the present invention, I propose to overcome completely the problems presented by this inherent tendency for a conveyer to creep laterally, and at the same time to relieve the in dividual helices of which the conveyer is fabricated and also the surface of the driving drum of all longitudinal strain, by utilizing the principle of action and reaction instead of attempting to oppose or to avoid such principle.

The principal object of my invention is to prevent lateral creepage of the article bearing strand of a conveyer fabricated from a plurality of transversely extending interconnected wire helices, by the provision of a support such as a driving mechanism embodying a drum or roller having a conveyer engaging surface which may move progressively in a direction transverse to the direction of travel of the conveyer throughout at least a portion of each rotation of the drum, in order to carry that portion of the conveyer which is in engagement with the drum in a lateral direction a distance sufllcient to prevent the helices of the conveyer as they successively move onto the drum and twist as they change their direction of movement in conforming to the curvature of the drum, from exerting a lateral thrust on the helices of the article bearing strand of the conveyer that are not yet in engagement with the drum, thus rendering it possible to avoid the expedients herelnabove discussed and to employ a conveyer fabricated entirely of helices wound in the same direction.

Another object of my invention is the provision of a conveyer driving mechanism, of the character described, embodying means for moving the conveyer engaging surface of the drum in a direction transverse to the direction of movement thereof, thus relieving the convolutions of the several helices of which the conveyer is fabricated of all lateral strain.

A further object of my invention is the provision of a conveyer driving mechanism, of the character described, embodying means actuated by the lateral movement of the article bearing strand of the conveyer for automatically controlling the distance that the conveyer engaging surface of the driving drum is moved laterally in accommodating the relative axial movement of the helices of the conveyer.

With such objects in view, as well as other advantages which may be incident to the use of the improvements, the invention consists of the parts and combinations thereof hereinafter set forth and claimed with the understanding that the several necessary elements constituting the same may be varied in proportion and arrangement without departing from the nature and scope of the invention as defined in the appended claims.

In order to make the invention more clearly understood there are shown in the accompanying drawings, means for carrying the invention into practical efiect, without limiting the improvements in their useful application to the particular construction, which for purpose of explanation have been made the subject of illustration.

In the accompanying drawings:

Figure 1 is a plan view of a conveyer driving mechanism constructed in accordance with my invention.

Figure 2 is a vertical longitudinal sectional view taken on line 22 of Figure 1, illustrating the construction of the pinch roller.

Figure 3 is a side elevational view of the mechanism shown in Figure 1.

Figure 4 is a vertical transverse sectional view taken on line 44 of Figure 1.

Figure 5 is a vertical transverse sectional view taken on line 55 of Figure 1.

Figure 6 is a vertical transverse sectional view taken on line 6-6 of Figure 1.

Figure '7 is a horizontal sectional view taken on line 7-7 of Figure 3.

Figure 8 is a plan view of a portion of a conveyer fabricated from a plurality of interconnected wire helices.

Figure 9 is a diagrammatic development view of the conveyer driving drum and conveyer.

Figure 10 is a plan view of the conveyer controlled adjusting mechanism.

Figure 11 is a fragmentary vertical sectional view taken on line 11-11 of Figure 10.

Referring to the drawings, the invention is shown as being embodied in a conveyer driving mechanism that is particularly adapted for use in connection with glass annealing lehrs, and for the purpose of illustration the amount of transverse or axial movement of the helices of the conveyer and the corresponding movement of the surface of the driving drum has been greatly exaggerated. This mechanism is shown as comprising a frame structure A; a sectional driving drum B; a conveyer C, composed entirely of interconnected wire helices wound in the same direction; a sectional pinch roll D; and a driving mechanism E.

The frame structure A comprises a pair of spaced side frame members 10 and 10 which are mounted upon a metallic base plate 11 supported by transversely extending channel bars 12 which vide a housing for the driving mechanism hereinafter to be described. The frame members 10 and 10" are also braced laterally by transversely extending upper and lower channel bars 14 and 15, respectively, which are secured to the forward ends of these members and by upper and lower channel bars 16 and 17 respectively which are secured to the rear ends of the frame members 10 and 10.

The driving drum B comprises hexagonal cast metal end members 18 (Figures 4, 5 and 7) having peripheral flanges 19 and formed with a plurality of bosses 20. Metallic plates 21 are secured to the flanges 19 of the end members 18 in any preferred manner, and are welded together along their adjacent edges to form a hollow hexagonal support having, a series of flat faces. By reason of the fact that the support is of polygonal cross-section, each of the plates 21 is reinforced throughout its length by the contiguous edges of the adjacent plates 21 and provides a very rigid yet comparatively light construction,

Gear wheels 22 and 22 provided with hubs 23 and 23* are secured to the end members 18 by bolts 24 engaging the bosses 20 thereof, and these gear wheels are mounted on a main supporting shaft 25 which extends entirely through the support and through axially disposed openings 26 formed in the end members 18, and is joumaled at its ends in bearings 27 and 27* formed in the side frame members 10 and 10 respectively.

Thrust bearings 28 and 28* are arranged interillustration I have shown the drum as having six sections having curved outer surfaces so that the several sections together complete a cylinder. The construction is such that the guides .29 and slides 31 cooperate to form a sliding connection between the several sections and the plates 21 of the hexagonal support, which permits the several sections to slide independently of one another on the hexagonal support in a direction transverse to the direction of rotation thereof,

- but at the same time preventing their displacement in I radial or circumferential directions. The several sections of the drum are thus, in effect, keyed to the support so as to transmit motion to the conveyer.

The several sections 32 of the drum are provided. with anti-slipping or tractive conveyer engaging surfaces each preferably consisting of a molded covering 33 of yieldable material such as rubber reinforced by fabric, and formed with inwardly extending flanges 34 (Figs. 4 and 5) adapted to embrace the outer edges of the section 32 and to be clamped to the inner surfaces thereof by removable clamping bars 35. Each of the coverings 33 is preferably provided with a plurality of bosses 36 for interlocking engagement with corresponding recesses formed in the outer curved surface of the associated section 32, so as to reduce creepage and stretching of the covering, and torelieve the edges of the covering of strain caused by its frictional driving engagement with the conveyer.

Cooperating with the driving drum B is the pinch roll D which is adapted to force the conveyer into positive driving engagement with the resilient surface of the drum so as to minimize slippage therebetween. This pinch roll D is shown as comprising two half cylindrical sections 37 and 37', which are mounted on a shaft 38 having a square intermediate portion 39 and cylindrical end portions 40 (Figs. 2 and 7), which arev journaled in bearing blocks 41 slidably mounted in ways 42 formed in the side frame members wand 10. The bearing blocks 41 are maintained against lateral displacement by plates 43 secured thereto for engagement with the sides of the ways 42, and the position of the bearing blocks 41 in the ways 42 may be adjusted by jack screws 44 so as to maintain the pinch roll D in gripping engagement with the conveyer. The sections 37 and 37': of the pinch roll are each formed with a longitudinally extending groove 45 through which the squared portion 39 of the shaft 38 extends, and the two sections are maintained against radial displacement by means of rings 46 which extend around the ends of the sections 37 and 37 and which are each secured to one of the sections for relative axial sliding engagement with the associated section. Suitable anti-friction devices, herein shown as comprising roller bearings 47, are disposed between the walls of the grooves 45 and the sides of the squared portion 39 of the shaft 38 and are maintained in proper spaced relation with respect to one another by spacing blocks 48 (Fig. 2) secured to the walls of the recesses 45. By means of this construction the pinch roll D is, in effect, keyed to the shaft 38, but the sections 37 and .37" thereof are free to slide in an axial direction a predetermined distance. The sections 37 and 37 of the pinch roll D are also each provided with an anti-slipping or tractive conveyer engaging surface preferably comprising a molded covering 49 (Fig. 4) of yieldable material such as rubber reinforced by fabric, which is formed with inwardly extending flanges 50 adapted to embrace the edges of the associated section and to be clamped to the inner surfaces thereof by removable clamping bars 51. The coverings 49 are also formed with bosses 52 for engagement with corresponding recesses provided in the outer curved surface of the associated section and tend to prevent localized strain on the covering when engaged by the conveyer.

The sections 37 and 37' of the pinch roll D are urged to the right, as viewed in Figure 2 of the drawings, by compression springs 53 which are disposed within recesses 54 formed in the sections 37 and 37 (Figs. 2 and 4), and which are interposed between slide blocks 55 which engage the right hand ends of the recesses and blocks 56 which are fixed to the squared portion 39 of the shaft 38. Axial movement of the sections 37 and 37' under the influence of the spring 53 is, however, limited by a stop in the form of a sleeve 57 carried by the right hand cylindrical portion 40 of the shaft 38 for abutting engagement by segof the sections 37 and 37.

As previously stated, the conveyer C comprises a plurality of interconnected wire helices 59 (Figures 4 and 10) and, as shown in Figure 4, the article bearing strand, adjacent to the end of its travel, is supported upon a table 60 which is herein shown as embodying a metal plate mounted upon the upper channel bar 16 of the frame structure A and reinforced by longitudinally extending bars 61. After leaving the table 60, the conveyer passes around the driving drum B, and between the driving drum and the pinch roll, and thence over the pinch roll, from which point the idle strand of the conveyer passes rearwardly to the point (not shown) where it again doubles back to perform its conveying function.

The driving drum B is rotated to draw the article bearing strand of the conveyer along its support, by means of the driving mechanism E which comprises two pinions 62 and 62 which are keyed to each end of a jack shaft 63 for intermeshing engagement with the gear wheels 22 and 22 The jack shaft 63 is journaled in bearings 64 provided on the side frame members 10 and 10, and has a worm gear 65 fixed to one end thereof for intermeshing engagement by a worm 66. The worm gear 65 extends through an opening 6'7 provided in the forward bracing plate 13 which is covered by a removable housing 68. The worm 66 is fixed to a transversely extending drive shaft 69 which is mounted in bearings '70 carried by the base plate 11 and which extends through the plate 13 to a point where it maybe connected with any suitable source of power.

The sections of the driving drum B which are in engagement with the conveyer are progressively and uniformly shifted transversely on the hexagonal support when the drum is rotated, by means of a ring cam 71 provided with a split '72. This-cam is formed with an opening '72 to accommodate the pinion 62 and is mounted on an annular cam carrier '73 in concentric relation with the drum B. The cam carrier '73 is formed with a peripheral flange '74 and with lugs '75 which extend radially inwardly and are secured to the side frame member 10 by means of bolts '76. One end of the cam '71 is pivotally mounted on the carrier '73 by a pivot pin or bolt '77, and the adjacent end of the cam '71 is sprung laterally so as to impart a helical configuration to the cam of the desired angularity or pitch by means of an adjusting or jack screw '78 provided with a hand wheel '79. This screw is threaded into a bearing provided on a bracket 81 which is bolted to the side frame member 10 Each of the sections 32 of the driving drum B is provided with a roller 82 for engagement with the inner vertical face of the cam '71, so that when the drum is rotated by means of the driving mechanism E, hereinbefore described, the rollers 82, as they follow the contour of the cam 71, will force the sections 32 transversely to the left, as viewed in Figures 1, 2 and '7. These sections 32 are urged to the right, as viewed in these figures, so as to maintain the rollers 82 in yieldable engagement with the cam '71, by means of tension springs 83 which are arranged in recesses 84 formed in the sections 32 (Figs. 4 and '7) Each of these springs is secured at one end to the associated section 32 of the driving drum by means of a clip 85, and at the other end thereof to the associated plate 21 of the hexagonal support, by means of a bracket 86. The sections 32 of the driving drum are thus caused to yieldably bear against the cam '71 at equally spaced points therearoun'd and with uniform pressure, and consequently the cam 71 will not move on its support during the rotation of the drum, but will remain in fixed position notwithstanding its single point of attachment '77 thereto. However, if desired, a plurality of relatively small backing screws 87 may be threaded into the cam '71 for abutting engagement with the flange 74 of the cam carrier '73, so as to insure that the cam will remain in proper position and will not rock on the carrier when it is traversed by the rollers 82.

The angularity of the cam '71 is adjusted so that it will force the sections 32 of the driving drum B in a transverse direction during the rotation of the drum a distance equal to the accumulative axial displacement of the helices of the conveyer in actual contact with the drum at any given time. For example, if the pitch of the helices 59 of which the conveyer is fabricated is one half inch and, as shown in the drawings, if the conveyer is in engagement with the drum throughout three quarters of its circumference, then the accumulative axial displacement of the helices 59 in contact with the drum will equal three eighths of an inch, and consequently the cam 71 will be adjusted so as to shift the sections 32 of the drum B transversely,a corresponding amount. moving the helices of the conveyer transversely instead of maintaining them fixed, as heretofore, no lateral motion is transmitted to that portion of the article bearing strand of the conveyer that is not in engagement with the drum. Lateral creeping of the article bearing strand of the conveyer on the supporting table 60 is thus prevented. Anti-friction devices may be disposed between the several sections 32 and the hexagonal support if desired, but in view of the fact that the sections 32 only move transversely a distance equal to three-fourths of the pitch distance of the helices By thus 59 during one rotation of the drum, the mechanical advantage of the cam is so great that the provision of such anti-friction devices may be unnecessary. For example, if the pitch distance of the helices 59 is three-eighths inch and the diameter of the cam 71 is twenty-four inches, the angularity of the cam '71 need only be approximately seventeen minutes fifty-four seconds in order to shift the sections 32 suificiently to accommodate the relative axial displacement of the helices 59.

Inasmuch as the pinch roll D is in clamping engagement with the conveyer, it may be desirable to permit the surface of this roll also to move transversely a distance equal to the transverse movement of the conveyer C and the sections 32 of the drum. This movement of the roll D is, however, very slight and may be accommodated by the spring of the wire helices or the yieldability of the coverings 33 and 49 of the drum and roller respectively, or by the combined yieldability of these elements. For example, in the case given above, if the total transverse movement of the sections of the drum is three eighths of an inch, the transverse movement of one of the sections of the pinch-roll will be one sixth of this distance or one sixteenth of an inch. Therefore, such a slight amount of lateral movement is well within the possible range of yieldability above described, and consequently it is practical to dispense with the sectional construction of the pinch roll if so desired. However, in the construction shown in the drawings, the sections of the pinch roll are moved positively in a direction transverse to the travel of the conveyer and uniformly with the transverse movement of the sections of the driving drum, by means of a plurality of arcuate 'pinch roll D. As soon, however, 'as the sections of the pinch roll move out of contact withthe flanges 88 they will be moved to the right under the influence of the springs 53 until they are arrested in their initial position by the end plates 58 engaging the stop sleeve 57. The sleeve 57 is of such length as will arrest the movement of the sections of the pinch roll at a point where the end plates 58 thereof are in proper position with respect to the flanges 88 of the driving drum, so that. as the drum and roll rotate, these flanges will successively engage the sides of the plates 58.

As soon as the sections 32 of the driving drum move out of engagement with the pinch roll and 'the conveyer, the rolls 82 ride off of the high portion of the cam 71 and the sections 32 are permitted to be returned to their initial or extreme right hand position under the influence of the springs 83.

determine whether or not the article bearing strand thereof moves laterally on the supporting table 60. If it is found that the conveyer after such initial adjustment evidences a tendency to creep laterally on the table 60 to the right, as viewed in the drawings, the angularity of the cam '11 is increased, the amount of adjustment of the cam being determined by the rate of creepage of the conveyer. If on the other hand, the conveyer evidences a tendency to creep toward the left, it will indicate that the sections 32 of the drum are being moved transversely a distance in excess to that necessary to ofiset the natural tendency of the conveyer to creep, and consequently the angularity of the: cam 71 is decreased. The cam 71 may thereafter be adjusted slightly one way or the other untfl' there is no evidence of a tendency for the conveyer to creep in either direction.

It may, however, be diflicult to thus adjust the cam '11 manually to the exact angularity which will prevent creepage,,and accordingly there is provided an instrumentality for automatically adjusting the angularity of the cam '71 during the operation of the mechanism. This instrumentality is shown as comprising a pair of guiding devices 89 and 89, carried by the table 60 and disposed one on each side of the conveyer C for engagement thereby. Each of these devices embodies an upper plate 90 which overhangs the adjacent edge of the conveyer to prevent the dis-. placement of the conveyer relative thereto, and which carries a pin 91 which extends vertically through a slot 92 in the table 60 .(Fig. 1) for engagement with one end of a connecting and spacing bar 93 extending transversely beneath the table 60. Each of the plates 90 also carries a pair of sprocket wheels 94 (Fig. 11) around which passes an endless sprocket chain 95 for engagement by the edge of the conveyer and which provides a yieldable abutment whereby friction between the edges of the conveyer and the guiding devices is minimizedf As viewed in Figures 1, 2 and 10 of the drawings, the left hand end of the bar 93 is connected to one end of a cable 96 which passes around a grooved pulley 97 carried by a bracket 98 fixed to the left hand side frame memer 10, thence across the mechanism beneath the table 60, thence over a pulley 99 carried by the bracket 81, thence downwardly and around a drum 100 which is fixed to the adjusting screw '78 and to which the cable is secured at an intermediate point, thence upwardly and over a pulley 101, also mounted on the bracket 81, and is secured at its opposite end to a turn buckle 102 which is secured to the right hand end of the bar 93. By means of this construction if the conveyer creeps in either direction it will automatically shift the position of the guiding devices89 and 89 which will cause a partial rotation of the adjusting screw '78 sufiicient to arrest such creepage. For example, if the conveyer should develop a creep toward the right, as viewed inFigure 1 of the drawings, it will engage the guiding device 89 and cause the partial rotation of the adjusting screw 78 in a clockwise direction, as viewed in Figure 3, soas to increase the angularity of the cam '71. As soon as the cam 71 has been thus adjusted sufficiently to arrest the creepage of the conveyer, the rotation of the adjusting screw '78 will cease and the parts will remain in their adjusted position. Conversely, if the conveyer should creep to the left, the adjusting screw will be rotated in a counterclockwise direction so as to decrease the angularity of the cam 71. As a result, the conveyer itself will effect a very accurate adjustment of the cam '71 during the operation of the mechanism. and until a point of equilibrium is reached at which there will be no tendency for the conveyer to creep in either direction. An automatic adjustment of the cam by the conveyer is thus obtained which will eliminate the necessity for the parts to be accurately adjusted manually and which will also obviate the necessity of observing the action of the conveyer from time to time in order to counteract creepage of the conveyer which may develop subsequent to the initial adjustmentof the cam 71., 7

From the foregoing it will be apparent that a very efficient driving mechanism for conveyers fabricated of interconnected wire helices is provided which will effectually prevent the creepage of the conveyer in either direction, and in which ly, of means for supporting said .conveyer where it changes its direction of travel and means acting independently of said conveyer for positivelyv moving said supporting means and that portion of said conveyer in engagement therewith progressively in a direction transverse to the direction of travel of said conveyer and in timed relation with the rate of said travel, an amount equal to the accumulative axial displacement of the to the direction'of travel of said conveyer and in timed relation with the rate of said travel, an amount equal to the accumulative axial displace ment of the helices of said conveyer in contact with said support caused by their screw action in changing their direction of travel.

3. In combination with a conveyer fabricated from a plurality of transversely extending interconnected wire helices, a driving mechanism therefor comprising a rotatable drum having a plurality of circumferentially arranged longitudinally extending conveyer supporting sections, and means operating independently of the conveyer for positively moving said sections in a direction transverse to the direction of rotation of said drum to move the conveyer in engagement therewith laterally a distance substantially equal to the lateral movement of said conveyer on said sections in conforming to the curvature of said drum.

4. In combination with a conveyer fabricated from a plurality of transversely extending interconnected wire helices, a driving mechanism therefor comprising a drum having a plurality of sections for supporting said conveyer throughout substantially the entire width thereof, and a cam for positively moving said sections parallel to the longitudinal axis of said drum to carry the conveyer in engagement therewith bodily in a lateral direction a distance substantially equal to the lateral movement of said conveyer on said sections inconforming to the curvature of saiddrum.

5. In combination with a conveyer fabricated from a plurality of transversely extending interconnected wire helices, a driving mechanism therefor comprising a drum having a plurality of conveyer engaging circumferential sections, and an annular cam mounted adjacent to one end of said drum and coaxially therewith for positively moving said sections parallel to the longitudinal axis of said drum to move the conveyer in engagement therewith laterally a distance substantially equal to the lateral movement of said conveyer in conforming to the curvature of said drum.

6. In combination with a conveyer fabricated from a plurality of transversely extending interconnected wire helices, a driving mechanism therefor comprising a drum having a plurality of circumferentially arranged conveyer supporting sections, an annular cam mounted adjacent to one end of said drum and coaxially therewith for positively moving said sections parallel to the longitudinal axis of said drum to carry the conveyer in engagement therewith bodily in a direction opposite to the direction of movement of said conveyer on said sections in conforming to the curvature of said drum; and means for adjusting the angularity of said cam to vary the degree of movement of said sections in accordance with the pitch distance of the convolutions of the helices of said conveyer.

'7. A driving mechanism for a conveyer fabrimovement of said conveyer for controlling said cated from a plurality of transversely extending interconnected wire helices, comprising a drum having a plurality of circumferentially arranged conveyer supporting sections, an annular split cam mounted adjacent to one end of said drum and coaxially therewith for positively moving said sections parallel to the longitudinal axis of said drum to carry the conveyer in engagement therewith, bodily in a direction opposite to the direction of movement of said conveyer on said sections in conforming to the curvature of said drum; and means for flexing said split cam to adjust the angularity thereof to vary the degree of movement imparted thereby to szid sections in accordance with the pitch distan e of the convolutions of the helices of said conveyer.

L 8. In combination with a conveyer fabricated from atplurality of interconnected wire helices and which changes its direction of travel vertically, of means for supporting said conveyer where it changes its direction of travel, adjustable means for positively moving said supporting means and that portion of said conveyer in engagement therewith progressively in a direction transverse to the direction of travel of said conveyer and in timed relation with the rate of said travel, an amount equal to the accumulative axial displacement of the helices of said conveyer in contact with said support caused by their screw action in changing their direction of travel, and 105 means controlled by the lateral movement of said conveyer for controlling the adjustment of said adjustable means.

9. In combination with a conveyer fabricated from a plurality of transversely extending inter- 1 connected wire helices, adriving mechanism for said conveyer comprising a sectional drum mounted for rotation about a horizontal axis and adapted to be frictionally engaged by said conveyer, an adjustable cam for positively moving the sections of said drum and'that portion of said conveyer in engagement therewith in a direction transverse to the direction of rotation thereof, andmeans controlled by the lateral movement of said conveyer for controlling the adjustment of 120 said cam.

10. In combination with a conveyer fabricated from a plurality of transversely extending interconnected wire helices, a driving mechanism therefor comprising a drum having a plurality 125 of conveyer supporting circumferentially arranged sections, an annular cam mounted adjacent to larity of said cam to vary the degree of movement of said sections in accordance with the pitch distance of the convolutions of the helices of said conveyer; and means controlled by the lateral adjusting means.

11. In combination with a conveyer fabricated from a plurality of transversely extending interconnected wire helices, a driving mechanism for said conveyer comprising a sectional drum mounted for rotation about a horizontal axis and adapted to be frictionally engaged by said conveyer, an annular flexible cam for moving the sections of said drum in a direction transverse to the direction of rotation thereof, and means con- 5 trolled by the lateral movement of said conveyer for flexing said cam to control the amount of transverse movement of said sections.

12. In combination with a conveyer fabricated from a plurality of transversely extending interconnected wire helices, a driving mechanism for said conveyer comprising a sectional drum mountedfor rotation about a horizontal axis, a sectional pinch roll for maintaining said conveyer in frictional engagement with said drum, an annular split cam arranged in concentric relation with said drum adjacent to one end thereof for moving said sections in a direction transverse to the direction of rotation of said drum, said cam having a fixed end and a movable end, an adjusting screw disposed in operative engagement with the movable end of said cam for flexing said cam to vary the angularity thereof and the transverse movement imparted thereby to the sections of said drum, and means controlled by lateral movement of said conveyer for operating said adjust:

ing screw to automatically control the angularity of said cam and the amount of the resultant transverse movement of said sections.

13. In combination with a conveyer fabricated from a plurality of transversely extending interconnected wire helices, a driving mechanism for said conveyer comprising a sectional drum mounted for rotation about a horizontal axis, a sectional pinch roll for maintaining said conveyer in frictional engagement with said drum,

an annular split cam arranged in concentric relation with said drum adjacent to one end thereof for moving said sections in a direction transverse to the direction of rotation of said drum, said cam having a fixed end and a movable end, an adjusting screw disposed in operative engagement with the movable end of said cam for flexing said cam to vary the angularity thereof and the transverse movement imparted thereby to the sections of said drum, means controlled by lateral movement of the article bearing strand of said conveyer that is not in engagement with said drum for operating said adjusting screw to automatically control the angularity of said cam and the amount of the resultant transverse movement of said sections, and means for returning the sections of said drum to their initial position when they rotate out of engagement with said conveyer.

14. A conveyer supporting roller comprising a plurality of longitudinally movable sections, and a molded tractive conveyer engaging covering for each of the sections provided with longitudinal ,flanges adapted to be removably secured to the associated section;

15. A conveyer supporting roller comprising a plurality of longitudinally movable sections provided with recesses in the outer surfaces thereof, and a molded tractive surface removably secured to each of said sections and provided with integral extensions for engagement with said recesses.

- MARSHALL LOW. 

